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EP1735673B1 - Method for monitoring a fuel supply device pertaining to an internal combustion engine - Google Patents

Method for monitoring a fuel supply device pertaining to an internal combustion engine Download PDF

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Publication number
EP1735673B1
EP1735673B1 EP05708024A EP05708024A EP1735673B1 EP 1735673 B1 EP1735673 B1 EP 1735673B1 EP 05708024 A EP05708024 A EP 05708024A EP 05708024 A EP05708024 A EP 05708024A EP 1735673 B1 EP1735673 B1 EP 1735673B1
Authority
EP
European Patent Office
Prior art keywords
fuel
pressure
regulator
pwm
fup
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP05708024A
Other languages
German (de)
French (fr)
Other versions
EP1735673A1 (en
Inventor
Erwin Achleitner
Martin Cwielong
Gerhard Eser
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Automotive GmbH
Original Assignee
VDO Automotive AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by VDO Automotive AG filed Critical VDO Automotive AG
Publication of EP1735673A1 publication Critical patent/EP1735673A1/en
Application granted granted Critical
Publication of EP1735673B1 publication Critical patent/EP1735673B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/20—Control of fluid pressure characterised by the use of electric means
    • G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
    • G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/22—Safety or indicating devices for abnormal conditions
    • F02D41/221—Safety or indicating devices for abnormal conditions relating to the failure of actuators or electrically driven elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/3809—Common rail control systems
    • F02D41/3836—Controlling the fuel pressure
    • F02D41/3845—Controlling the fuel pressure by controlling the flow into the common rail, e.g. the amount of fuel pumped
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/3809—Common rail control systems
    • F02D41/3836—Controlling the fuel pressure
    • F02D41/3863—Controlling the fuel pressure by controlling the flow out of the common rail, e.g. using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/14—Introducing closed-loop corrections
    • F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
    • F02D2041/1409—Introducing closed-loop corrections characterised by the control or regulation method using at least a proportional, integral or derivative controller
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/22—Safety or indicating devices for abnormal conditions
    • F02D2041/224—Diagnosis of the fuel system

Definitions

  • the driver of the motor vehicle is informed about the malfunction, so that this can cause a check and possibly repair in a workshop.
  • the monitoring device of the internal combustion engine stores information about the errors that have occurred, such as the type of error, the location of the fault and the operating conditions under which the malfunction has occurred. This information can be evaluated in a workshop and thus support the repair work.
  • the object of the invention is to provide a method which reliably monitors fuel supply devices of internal combustion engines.
  • the invention is characterized by a method for monitoring a fuel supply device of an internal combustion engine, wherein the fuel supply means a low pressure circuit, a high-pressure pump, which is input side coupled to the low pressure circuit and the fuel in a fuel storage, a volume flow control valve, which is associated with the high-pressure pump, and a electromechanical pressure regulator, which is operatively connected to the fuel storage and the low-pressure circuit and the fuel from the fuel storage in the low-pressure circuit can divert includes.
  • a control signal for the volume flow control valve is generated in a first mode by means of a first controller, the first controller comprises at least one integral component and the first controller is supplied as a control difference, a difference of a predetermined fuel pressure and a detected fuel pressure.
  • a control signal for the electromechanical pressure regulator is generated by means of a second controller, wherein the difference between the predetermined fuel pressure and the detected fuel pressure is supplied to the second controller as the control difference.
  • an error in the Kraftstaffzugot reinforced is detected depending on the integral component of the first controller.
  • an error in the fuel supply device is detected as a function of the detected fuel pressure and the actuating signal for the electromechanical pressure regulator.
  • the advantage is that fuel supply devices, which have both a volume flow control valve and an electro-mechanical pressure regulator, can be reliably monitored. Errors in components of the fuel supply can be easily detected. The procedure used the devices required anyway to control the fuel pressure in the fuel storage and requires no additional components to the fuel supply.
  • an error in the fuel supply device is detected in the first mode when the integral component of the first controller is smaller than a predetermined lower tolerance limit of the integral component or greater than a predetermined upper tolerance limit of the integral component.
  • a further preferred embodiment of the method is characterized in that in the second mode of operation an error in the fuel supply device is detected if the detected fuel pressure is less than a lower tolerance limit for the fuel pressure predetermined by the control signal for the electromechanical pressure regulator or greater than one from the actuating signal for the electromechanical pressure regulator predetermined upper tolerance limit for the fuel pressure.
  • the force toffzu slaughter grounds is equipped with a combination valve, which comprises the flow control valve and the electro-mechanical pressure regulator and has a common actuator for the flow control valve and the electro-mechanical pressure regulator.
  • the method sets by means of the combination valve, the first mode in that the current value of a common control signal is in a first range of values of the common control signal, or sets the second mode in that the current value of the common control signal in a second range of values the common control signal is located.
  • An internal combustion engine ( FIG. 1 ) includes an intake manifold 1, an engine block 2, a cylinder head 3, and an exhaust tract 4.
  • the engine block 2 includes a plurality of cylinders having pistons and connecting rods via which they are coupled to a crankshaft 21.
  • the cylinder head 3 includes a valvetrain with a gas inlet valve, a gas outlet valve and valve actuators.
  • the cylinder head 3 further includes an injection valve 34 and a spark plug.
  • a feed device 5 is provided for fuel. It comprises a fuel tank 50, which is connected via a first fuel line with a low-pressure pump 51 is. The fuel line opens into a swirl pot 50a. On the output side, the low pressure pump 51 is operatively connected to an inlet 53 of a high pressure pump 54. Furthermore, on the output side of the low-pressure pump 51, a mechanical regulator 52 is provided, which is connected on the output side via a further fuel line to the fuel tank 50. The low-pressure pump 51, the mechanical regulator 52, the fuel line, the further fuel line and the inlet 53 form a low-pressure circuit.
  • the low-pressure pump 51 is preferably designed so that it always supplies a sufficiently high fuel quantity during operation of the internal combustion engine, which ensures that a predetermined low pressure is not exceeded.
  • the inlet 53 is guided to the high-pressure pump 54, which promotes the fuel on the output side to a fuel reservoir 55.
  • the high pressure pump 54 is usually driven by the camshaft and thus promotes a constant fuel volume at constant speed of the crankshaft 21 into the fuel accumulator 55.
  • the injection valves 34 are operatively connected to the fuel reservoir 55.
  • the fuel is thus supplied to the injection valves 34 via the fuel accumulator 55.
  • a volume flow control valve 56 is provided, by means of which the volume flow can be adjusted, which is the high-pressure pump 54 is supplied.
  • a predetermined fuel pressure FUF_SP in the fuel accumulator 55 can be set.
  • the fuel supply device 5 with an electromagnetic pressure regulator 57 on the output side of the fuel accumulator 55 and with a return line in the Low pressure circuit provided. If a fuel pressure in the fuel accumulator 55 is greater than the fuel pressure FUP_SP predetermined by corresponding actuation of the electromechanical pressure regulator 57, the electromechanical pressure regulator 57 opens and fuel is discharged from the fuel accumulator 55 into the low pressure circuit.
  • volume flow control valve 56 may be integrated into the high-pressure pump 54, or the electro-mechanical pressure regulator 57 and the flow control valve 56 are set via a common actuator, as exemplified in FIG. 2 shown and explained in more detail below.
  • the internal combustion engine is assigned a control device 6, which in turn are assigned sensors that detect different measured variables and in each case determine the measured value of the measured variable.
  • the control device 6 determines dependent on at least one of the measured variables manipulated variables, which are then converted into corresponding control signals for controlling actuators by means of corresponding actuators.
  • the sensors are, for example, a pedal position sensor which detects the position of an accelerator pedal, a crankshaft angle sensor which detects a crankshaft angle and which is then assigned an engine speed, an air mass meter and a fuel pressure sensor 58 which detects a fuel pressure FUP_AV in the fuel accumulator 55.
  • a pedal position sensor which detects the position of an accelerator pedal
  • a crankshaft angle sensor which detects a crankshaft angle and which is then assigned an engine speed
  • an air mass meter and a fuel pressure sensor 58 which detects a fuel pressure FUP_AV in the fuel accumulator 55.
  • any subset of the sensors or additional sensors may be present.
  • the actuators are designed, for example, as gas inlet or gas outlet valves, injection valves 34, spark plug, throttle valve, low-pressure pump 51, volume flow control valve 56 or else as electromechanical pressure regulator 57.
  • the internal combustion engine also has other cylinders, which are then assigned corresponding actuators.
  • FIG. 2 shows a combination valve 7, which includes an actuator 70, the flow control valve 56 and the electro-mechanical pressure regulator 57.
  • the combination valve 7 has an outlet 71 operatively connected to the inlet of the high pressure pump 54, a port 72 operatively connected to the inlet 53, and an inlet 73 operatively connected to the fuel reservoir 55.
  • the flow control valve 56 includes the port 72, the outlet 71, a valve actuator 74, and the actuator 70.
  • the electro-mechanical pressure regulator 57 includes the inlet 73, the port 72, the valve actuator 74, a spring 75, a valve plug 76, and the actuator 70.
  • the actuator 70 moves in response to a control signal PWM the valve actuator 74 in the axial direction.
  • the spring 75 is disposed between the valve actuator 74 and the valve closure 76 and biased depending on the axial position of the valve actuator 74.
  • the valve actuator 74 is designed such that, in the region of a first axial displacement of the valve actuator 74 in the direction of the spring 75, starting from its axial position, in which it is pressed by the spring 75, without the actuation of the actuator 70 with the control signal PWM, the fuel flow is substantially prevented. In this state, only a leakage flow from the port 72 to the outlet 71.
  • the port 72 is hydraulically coupled to the outlet 71.
  • a differently large volume flow can flow from the inlet 53 into the port 72 towards the outlet 71 and to the high-pressure pump 54.
  • the inlet 73 is hydraulically coupled to the port 72 such that fuel from the fuel accumulator 55 into the inlet 73 toward the outlet 72 in the inlet 53 can flow.
  • the fuel pressure in the fuel accumulator 55 which is at least necessary for opening the electro-mechanical pressure regulator, can be adjusted by increasing or decreasing the control signal PWM.
  • the actuator 70 correspondingly increases or decreases the force that acts on the spring 75 via the valve actuator 74 and biases the spring 75.
  • the force caused by the bias of the spring 75 closes the electro-mechanical pressure regulator when the force exerted by the fuel pressure in the fuel accumulator 55 on the valve closure 76 is smaller.
  • FIG. 3 shows characteristics of the in FIG. 2
  • a pressure curve 80 shows the relationship between the control signal PWM in amperes and the fuel pressure in the fuel tank 55 in bar. If the fuel pressure in the fuel accumulator 55 is increased above the value predefined by the pressure curve 80 at a given control signal PWM, the electromechanical pressure regulator 57 opens and reduces the fuel pressure in the fuel accumulator 55 by discharging fuel from the fuel accumulator 55 into the inlet 53.
  • a threshold which in this embodiment has a value of about 0.5 amperes
  • the diagram shows an upper flow curve 81, which represents an upper tolerance limit for the combination valve 7, a lower flow curve 82, which is a lower tolerance limit for the combination valve 7, and a mean flow curve 83, which represents the mean value between the upper and lower flow curves.
  • the flow curves 81, 82 and 83 show that in this embodiment, below the threshold value, that is, when the volume flow control valve 56 is substantially closed, the leakage flow can still flow.
  • FIG. 4 1 is a block diagram of a control device that may be used to control the fuel pressure in a fuel supply device 5 that includes a combination valve 7, as exemplified in FIG FIG. 2 is executed.
  • the regulation of the fuel pressure in the fuel accumulator 55 is dependent on in which mode the fuel supply device 5 is currently operated.
  • a first mode the fuel pressure in the fuel accumulator 55 is adjusted depending on the amount of fuel delivered by the high-pressure pump 54.
  • the volume flow control valve 56 is open and the amount of fuel delivered is dependent on the control of the volume flow control valve 56.
  • the electro-mechanical pressure regulator 57 is closed. When more fuel is delivered to the fuel reservoir 55 than is metered, the fuel pressure in the fuel reservoir 55 increases. If less fuel is delivered to the fuel reservoir 55 than is metered, then the fuel pressure in the fuel reservoir 55 decreases correspondingly.
  • This first mode is called volume control VC.
  • the volume flow control valve 56 is closed. By the flow control valve 56, only the leakage flow. If the electromechanical pressure regulator 57 is closed and less fuel is metered as is conveyed by the leakage flow in the fuel accumulator 55, then the fuel pressure in the fuel accumulator 55 increases until the electro-mechanical pressure regulator 57 opens and Fuel in the inlet 53 ab interviewedt. As a result, the fuel pressure in the fuel accumulator 55 is limited to the fuel pressure predetermined by the electromechanical pressure regulator 57. This second mode is therefore called pressure control PC.
  • FIG. 4 shows two control circuits, between which, depending on the currently set operating mode of the fuel supply device 5 by means of a switch LV_MS can be switched. If the currently set operating mode is the first operating mode, ie the quantity control VC, then the switch LV_MS is in the position VC. If the currently set operating mode is the second operating mode, ie the pressure control PC, then the LV_MS switch is in the PC position.
  • a control difference FUP_DIF is determined from the difference between the predetermined fuel pressure FUP_SP and the detected fuel pressure FUP_AV.
  • the control difference FUP_DIF is supplied to a controller in block B1 in the quantity control VC.
  • This controller comprises at least one integral component I_CTRL and is preferably designed as a PI controller.
  • a controller value FUEL_MASS_FB_CTRL of the first controller is determined.
  • a pilot value FUEL_MASS_PRE of the fuel mass to be delivered is determined in a block B2.
  • the pilot value FUEL_MASS_PRE of the fuel mass to be delivered, the controller value FUEL_MASS_FB_CTRL of the first controller and the fuel mass MFF to be injected are added up to a fuel mass FUEL_MASS_REQ to be delivered.
  • an actuating signal PWM_VC is determined during flow control VC.
  • the block B3 preferably includes a map.
  • a block B4 represents the in FIG. 1 shown fuel supply device 5 with the in FIG. 2 shown combination valve 7.
  • the control signal PWM which is equal to the control signal PWM_VC at volume control VC in volume control, is the Input size of block B4.
  • the output of the block B4 is the detected fuel pressure FUP_AV detected by the fuel pressure sensor 58, for example.
  • the control difference FUP_DIF is fed to a second controller in a block B5.
  • the controller in block B5 preferably comprises a PI controller.
  • a pilot control value PWM_PRE for an actuating signal PWM_PC is determined in pressure control PC, to which a controller value PWM_FB_CTRL of the second controller determined in block B5 is added.
  • the sum is the control signal PWM_PC with pressure control PC.
  • the control signal PWM is equal to the control signal PWM_PC with pressure control PC.
  • the block B6 preferably includes a map.
  • the maps of blocks B3 and B6 are preferably determined in advance by tests on an engine test bench, by simulations or by driving tests. Alternatively, for example, functions based on physical models may also be used.
  • FIG. 4 The block diagram shown is a preferred embodiment of a control device for a fuel supply device 5 with a combination valve 7 after FIG. 2 and characteristics after FIG. 3 , If, however, the volumetric flow control valve 56 and the electromechanical pressure regulator 57 each have their own actuator, then the control signal PNM_VC acts on the actuator of the volume flow control valve 56 and the control signal PWM_PC at pressure control PC on the actuator of the electro-mechanical pressure regulator 57 in the flow control VC.
  • the block B4 Consequently, instead of the common control signal PWM both the control signal PWM_VC supplied with volume control VC and the control signal PWM_PC in pressure control PC.
  • the control circuits for the first and the second mode of operation in this case preferably operate in parallel, so that in the FIG. 4 shown Switch LV_MS can be dispensed with.
  • the blocks B1 and B5 are simultaneously fed with the control difference FUP_DIF.
  • FIG. 5 shows a flowchart for detecting errors in a fuel supply device 5 of an internal combustion engine.
  • the method is started in a step S1.
  • the step S1 is executed at the start of the internal combustion engine.
  • the step S1 preferably comprises further, not shown here, initialization steps, such as a reset of counters.
  • step S2 the position of the switch LV_MS is checked. If there is no switch LV_MS, then the current operating mode of the fuel supply device 5 is determined in step S2.
  • the detected fuel pressure FUP__AV is checked in a step S3. If the detected fuel pressure FUP_AV is greater than or equal to a predefined lower tolerance limit FUP_PMM_BOL for the fuel pressure FUP_AV and less than or equal to a predetermined upper tolerance limit FUP_PMW_TOL for the fuel pressure FUP_AV, then no exit of the value range specified by the tolerance limits FUP_PWM_BOL and FUP_PWM_TOL is recognized and the processing in a step S4 continues.
  • step S3 If the detected fuel pressure FUP_AV is outside the value range specified by the tolerance limits FUP_PWM_BOL and FUP_PWM_TOL in step S3, an error may be present and the processing is continued in a step S5.
  • step S4 for example, the error counters are checked and optionally provided with a new value. The error counters are reduced by a predetermined amount, for example.
  • T_W After the step S4, the processing after a waiting period T_W is continued again in the step S2. If the condition of step S3 is not met, an error counter PWM_ERR_CNT of the control signal PWM is increased in step S5, for example by one.
  • the integral component I_CTRL of the first controller in block B1 is checked in a step S6 following step S2. If the integral component I_CTRL is greater than or equal to a predetermined lower tolerance limit I_CTRL_BOL of the integral component and less than or equal to a predetermined upper tolerance limit I_CTRL__TOL of the integral component, then no exit of the value range specified by the tolerance limits I_CTRL_BOL and I_CTRL_TOL is detected and the processing is continued in step S4. Otherwise, the processing is continued in a step S7. After the step S4, the processing is continued after the waiting time T__W in the step S2. If the condition of step S6 is not satisfied, then in step S7 an error counter I_CTRL_ERR_CNT of the integral component I_CTRL is increased, e.g. at 1.
  • step S8 The stepping-up of the error counter in step S5 or step S7 is followed by step S8 in which the values of the error counters are checked. If the error counter PWM_ERR_CNT of the control signal PWM is greater than or equal to a predetermined upper error limit PWM_ERR_CNT_TOL of the error counter PWM_ERR_CNT of the control signal PWM or if the error counter I_CTRL__ERR_CNT of the integral component I_CTRL is greater than or equal to a predetermined upper error limit I_CTRL_ERR_CNT_TOL of the error counter I_CTRL_ERR_CNT of the integral component I_CTRL, then an error is detected and In a step S9 measures are taken which register and store, for example, the exact location of the fault and the fault conditions, ensure safe operation of the internal combustion engine and report the fault to the driver of the motor vehicle. If no exceeding of the error limits PWM__ERR_CNT_TOL and I_CTRL_ERR_
  • no error counters are provided. In this case, an error is immediately recognized when the conditions in the step S3 or in the step S6 are not satisfied.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention relates to a fuel supply device pertaining to an internal combustion engine, said device comprising a low pressure circuit, a high pressure pump that is coupled to the low pressure circuit on the input side and transports the fuel into a fuel accumulator, a volume flow control valve associated with the high pressure pump, and an electromechanical pressure regulator that is actively connected to the fuel accumulator and the low pressure circuit, and can stop the flow of fuel from the fuel accumulator into the low pressure circuit. Said fuel supply device has a regulating device comprising a first regulator (B1) which is provided with at least one integral part and which produces, in a first mode of operation, a regulating signal (PWM_VC) for the volume flow control valve, and a second regulator (B5) that produces a regulating signal (PWM_PC) for the electromechanical pressure regulator in a second mode of operation. In the first mode of operation, an error in the fuel supply device is identified according to the integral part of the first regulator (B1). In the second mode of operation, an error in the fuel supply device is identified according to a detected fuel pressure (FUP_AV) and the regulating signal (PWM_PC) for the electromechanical pressure regulator.

Description

Die Anforderungen an Brennkraftmaschinen, insbesondere in Kraftfahrzeugen, steigen aufgrund von gesetzlichen Bestimmungen bezüglich Schadstoffemissionen und aufgrund von Kundenwünschen hinsichtlich Zuverlässigkeit, effizientem Einsatz der Betriebsmittel, insbesondere von Kraftstoff, und geringen Wartungskosten. Diese Anforderungen können nur dann erfüllt werden, wenn Fehlfunktionen von Fahrzeugkomponenten zuverlässig und genau erkannt und protokolliert werden, so dass Fehlfunktionen ausgeglichen oder eine Reparatur der fehlerbehafteten Fahrzeugkomponenten veranlasst werden können. Zu diesem Zweck werden Fahrzeugkomponenten, insbesondere alle abgasrelevanten Fahrzeugkomponenten, wie zum Beispiel die Katalysatoranlage, die Lambdasonde und das gesamte Kraftstoffsystem, überwacht. Durch die Überwachungsmaßnahmen soll ein schadstoffarmer Betrieb sichergestellt und die Fahrsicherheit aufrecht erhalten werden. Dazu gehört, dass bei dem Auftreten von Fehlern ein Notlauf der Brennkraftmaschine sichergestellt und Folgeschäden vermieden werden können. Der Fahrer des Kraftfahrzeugs wird über die Fehlfunktion informiert, so dass dieser eine Überprüfung und gegebenenfalls Reparatur in einer Werkstatt veranlassen kann. Die Überwachungseinrichtung der Brennkraftmaschine speichert Informationen über die aufgetretenen Fehler, wie zum Beispiel die Fehlerart, den Fehlerort und die Betriebsbedingungen, unter denen die Fehlfunktion aufgetreten ist. Diese Informationen können in einer Werkstatt ausgewertet werden und unterstützen so die Reparaturarbeiten.The requirements for internal combustion engines, in particular in motor vehicles, are increasing due to legal regulations regarding pollutant emissions and due to customer requirements with regard to reliability, efficient use of the equipment, in particular of fuel, and low maintenance costs. These requirements can only be met if malfunctions of vehicle components are reliably and accurately detected and logged, so that malfunctions can be compensated for or a repair of the faulty vehicle components can be initiated. For this purpose, vehicle components, in particular all exhaust-relevant vehicle components, such as the catalyst system, the lambda probe and the entire fuel system, monitored. The monitoring measures should ensure low-emission operation and maintain driving safety. This includes ensuring an emergency run of the internal combustion engine when faults occur and consequential damage can be avoided. The driver of the motor vehicle is informed about the malfunction, so that this can cause a check and possibly repair in a workshop. The monitoring device of the internal combustion engine stores information about the errors that have occurred, such as the type of error, the location of the fault and the operating conditions under which the malfunction has occurred. This information can be evaluated in a workshop and thus support the repair work.

Herkömmliche Überwachungseinrichtungen für Brennkraftmaschinen sind aus den Druckschriften DE 101 36 706 A1 , DE 197 57 594 A1 , US 6,234,148 B1 , DE 101 62 989 C1 und US 6,055,961 zu entnehmen.Conventional monitoring devices for internal combustion engines are from the documents DE 101 36 706 A1 . DE 197 57 594 A1 . US 6,234,148 B1 . DE 101 62 989 C1 and US 6,055,961 refer to.

Die Aufgabe der Erfindung ist, ein Verfahren anzugeben, das Kraftstoffzuführeinrichtungen von Brennkraftmaschinen zuverlässig überwacht.The object of the invention is to provide a method which reliably monitors fuel supply devices of internal combustion engines.

Die Aufgabe wird gelöst durch die Merkmale der unabhängigen Patentansprüche. Vorteilhafte weiterbildungen der Erfindung sind in den Unteransprüchen gekennzeichnet.The object is solved by the features of the independent claims. Advantageous developments of the invention are characterized in the subclaims.

Die Erfindung zeichnet sich aus durch ein Verfahren zum Überwachen einer Kraftstoffzuführeinrichtung einer Brennkraftmaschine, wobei die Kraftstoffzuführeinrichtung einen Niederdruckkreis, eine Hochdruckpumpe, die eingangsseitig gekoppelt ist mit dem Niederdruckkreis und die Kraftstoff in einen Kraftstoffspeicher fördert, ein Volumenstromsteuerventil, das der Hochdruckpumpe zugeordnet ist, und einen elektromechanischen Druckregulator, der mit dem Kraftstoffspeicher und dem Niederdruckkreis wirkverbunden ist und der Kraftstoff aus dem Kraftstoffspeicher in den Niederdruckkreis absteuern kann, umfasst. Bei dem Verfahren wird in einer erstern Betriebsart mittels eines ersten Reglers ein Stellsignal für das Volumenstromsteuerventil erzeugt, wobei der erste Regler mindestens einen Integralanteil umfasst und dem ersten Regler als eine Regeldifferenz eine Differenz eines vorgegebenen Kraftstoffdrucks und eines erfassten Kraftstoffdrucks zugeführt wird. In einer zweiten Betriebsart wird mittels eines zweiten Reglers ein Stellsignal für den elektromechanischen Druckregulator erzeugt, wobei dem zweiten Regler als die Regeldifferenz die Differenz des vorgegebenen Kraftstoffdrucks und des erfassten Kraftstoffdrucks zugeführt wird. In der ersten Betriebsart wird auf einen Fehler in der Kraftstaffzuführeinrichtung erkannt abhängig von dem Integralanteil des ersten Reglers. In der zweiten Betriebsart wird auf einen Fehler in der Kraftstoffzuführeinrichtung erkannt abhängig von dem erfassten Kraftstoffdruck und dem Stellsignal für den elektromechanischen Druckregulator.The invention is characterized by a method for monitoring a fuel supply device of an internal combustion engine, wherein the fuel supply means a low pressure circuit, a high-pressure pump, which is input side coupled to the low pressure circuit and the fuel in a fuel storage, a volume flow control valve, which is associated with the high-pressure pump, and a electromechanical pressure regulator, which is operatively connected to the fuel storage and the low-pressure circuit and the fuel from the fuel storage in the low-pressure circuit can divert includes. In the method, a control signal for the volume flow control valve is generated in a first mode by means of a first controller, the first controller comprises at least one integral component and the first controller is supplied as a control difference, a difference of a predetermined fuel pressure and a detected fuel pressure. In a second mode, a control signal for the electromechanical pressure regulator is generated by means of a second controller, wherein the difference between the predetermined fuel pressure and the detected fuel pressure is supplied to the second controller as the control difference. In the first mode, an error in the Kraftstaffzuführeinrichtung is detected depending on the integral component of the first controller. In the second mode of operation, an error in the fuel supply device is detected as a function of the detected fuel pressure and the actuating signal for the electromechanical pressure regulator.

Der Vorteil ist, dass Kraftstoffzuführeinrichtungen, die sowohl ein Volumenstromsteuerventil als auch einen elektromechanischen Druckregulator haben, zuverlässig überwacht werden können. Fehler in Komponenten der Kraftstoffzuführeinrichtung können auf einfache Weise erkannt werden. Das verfahren verwendet die zur Regelung des Kraftstoffdrucks im Kraftstoffspeicher ohnehin benötigten Einrichtungen und erfordert keine zusätzlichen Komponenten an der Kraftstoffzuführeinrichtung.The advantage is that fuel supply devices, which have both a volume flow control valve and an electro-mechanical pressure regulator, can be reliably monitored. Errors in components of the fuel supply can be easily detected. The procedure used the devices required anyway to control the fuel pressure in the fuel storage and requires no additional components to the fuel supply.

Vorteilhafterweise wird in der ersten Betriebsart ein Fehler in der Kraftstoffzuführeinrichtung erkannt, wenn der Integralanteil des ersten Reglers kleiner ist als eine vorgegebene untere Toleranzgrenze des Integralanteils oder größer ist als eine vorgegebene obere Toleranzgrenze des Integralanteils. Dieses Verfahren hat den Vorteil, dass auch bei instationärem Betrieb der Brennkraftmaschine Fehler in der Kraftstoff zuführeinrichtung erkannt werden können, wenn der Kraftstoffdruck im Kraftstoffspeicher nicht konstant ist.Advantageously, an error in the fuel supply device is detected in the first mode when the integral component of the first controller is smaller than a predetermined lower tolerance limit of the integral component or greater than a predetermined upper tolerance limit of the integral component. This method has the advantage that even in unsteady operation of the internal combustion engine errors in the fuel supply device can be detected when the fuel pressure in the fuel tank is not constant.

Eine weitere bevorzugte Ausführungsform des Verfahrens zeichnet sich dadurch aus, dass in der zweiten Betriebsart ein Fehler in der Kraftstoffzuführeinrichtung erkannt wird, wenn der erfasste Kraftstoffdruck kleiner ist als eine von dem Stellsignal für den elektromechanischen Druckregulator vorgegebene untere Toleranzgrenze für den Kraftstoffdruck oder größer ist als eine von dem Stellsignal für den elektromechanischen Druckregulator vorgegebene obere Toleranzgrenze für den Kraftstoffdruck. Dies hat den Vorteil, dass fehlerhafte Komponenten der Kraftstoffzuführeinrichtung auf sehr einfache Weise erkannt werden können.A further preferred embodiment of the method is characterized in that in the second mode of operation an error in the fuel supply device is detected if the detected fuel pressure is less than a lower tolerance limit for the fuel pressure predetermined by the control signal for the electromechanical pressure regulator or greater than one from the actuating signal for the electromechanical pressure regulator predetermined upper tolerance limit for the fuel pressure. This has the advantage that faulty components of the fuel supply device can be detected in a very simple manner.

Gemäß einer Weiterbildung der Erfindung ist die Krafts toffzuführeinrichtung mit einem Kombinationsventil ausgestattet, das das Volumenstromsteuerventil und den elektromechanischen Druckregulator umfasst und das einen gemeinsamen Stell antrieb für das Volumenstromsteuerventil und den elektromechanischen Druckregulator hat. Das Verfahren stellt mittels des Kombinationsventils die erste Betriebsart dadurch ein, dass der aktuelle Wert eines gemeinsamen Stellsignals in einem ersten Wertebereich des gemeinsamen Stellsignals liegt, oder stellt die zweite Betriebsart dadurch ein, dass der aktuelle Wert des gemeinsamen Stellsignals in einem zweiten Wertebereich des gemeinsamen Stellsignals liegt. Ein Vorteil dieses Verfahrens ist, dass eine hohe Zuverlässigkeit und eine einfache Ansteuerung des Kombinationsventils möglich ist. Dadurch werden Kosten gespart.According to one embodiment of the invention, the force toffzuführeinrichtung is equipped with a combination valve, which comprises the flow control valve and the electro-mechanical pressure regulator and has a common actuator for the flow control valve and the electro-mechanical pressure regulator. The method sets by means of the combination valve, the first mode in that the current value of a common control signal is in a first range of values of the common control signal, or sets the second mode in that the current value of the common control signal in a second range of values the common control signal is located. An advantage of this method is that high reliability and easy control of the combination valve is possible. This saves costs.

Ausführungsbeispiele der Erfindung sind im Folgenden anhand der schematischen Zeichnungen erläutert. Es zeigen:

Figur 1
eine Brennkraftmaschine mit einer Kraftstoffzuführeinrichtung,
Figur 2
ein Kombinationsventil, das ein Volumenstromsteuerventil und einen elektromechanischen Druckregulator mit einem gemeinsamen Stellantrieb umfasst,
Figur 3
die Kennlinie des Kombinationsventils aus Figur 2,
Figur 4
das Blockschaltbild einer Regeleinrichtung zur Regelung des Kraftstoffdrucks in einem Kraftstoffspeicher, und
Figur 5
ein Ablaufdiagramm zur Erkennung von Fehlern in der Kraftstoffzuführeinrichtung.
Embodiments of the invention are explained below with reference to the schematic drawings. Show it:
FIG. 1
an internal combustion engine having a fuel supply device,
FIG. 2
a combination valve comprising a volumetric flow control valve and an electromechanical pressure regulator with a common actuator,
FIG. 3
the characteristic of the combination valve FIG. 2 .
FIG. 4
the block diagram of a control device for controlling the fuel pressure in a fuel storage, and
FIG. 5
a flowchart for detecting errors in the fuel supply.

Elemente gleicher Konstruktion und Funktion sind figurenübergreifend mit den gleichen Bezugszeichen versehen.Elements of the same construction and function are provided across the figures with the same reference numerals.

Eine Brennkraftmaschine (Figur 1) umfasst einen Ansaugtrak-t 1, einen Motorblock 2, einen zylinderkopf 3 und einen Abgas-trakt 4. Der Motorblock 2 umfasst mehrere Zylinder, welche Kolben und Pleuelstangen haben, über die sie mit einer Kurbelwelle 21 gekoppelt sind.An internal combustion engine ( FIG. 1 ) includes an intake manifold 1, an engine block 2, a cylinder head 3, and an exhaust tract 4. The engine block 2 includes a plurality of cylinders having pistons and connecting rods via which they are coupled to a crankshaft 21.

Der Zylinderkopf 3 umfasst einen Ventiltrieb mit einem Gaseinlassventil, einem Gasauslassventil und Ventilantrieben. Der Zylinderkopf 3 umfasst ferner ein Einspritzventil 34 und eine Zündkerze.The cylinder head 3 includes a valvetrain with a gas inlet valve, a gas outlet valve and valve actuators. The cylinder head 3 further includes an injection valve 34 and a spark plug.

Ferner ist eine zuführeinrichtung 5 für Kraftstoff vorgesehen. Sie umfasst einen Kraftstofftank 50, der über eine erste Kraftstoffleitung mit einer Niederdruckpumpe 51 verbunden ist. Die Kraftstoffleitung mündet in einen Schwalltopf 50a. Ausgangsseitig ist die Niederdruckpumpe 51 mit einem Zulauf 53 einer Hochdruckpumpe 54 wirkverbunden. Ferner ist auch ausgangsseitig der Niederdruckpumpe 51 ein mechanischer Regulator 52 vorgesehen, welcher ausgangsseitig über eine weitere Kraftstoffleitung mit dem Kraftstofftank 50 verbunden ist. Die Niederdruckpumpe 51, der mechanische Regulator 52, die Kraftstoffleitung, die weitere Kraftstoffleitung und der Zulauf 53 bilden einen Niederdruckkreis.Furthermore, a feed device 5 is provided for fuel. It comprises a fuel tank 50, which is connected via a first fuel line with a low-pressure pump 51 is. The fuel line opens into a swirl pot 50a. On the output side, the low pressure pump 51 is operatively connected to an inlet 53 of a high pressure pump 54. Furthermore, on the output side of the low-pressure pump 51, a mechanical regulator 52 is provided, which is connected on the output side via a further fuel line to the fuel tank 50. The low-pressure pump 51, the mechanical regulator 52, the fuel line, the further fuel line and the inlet 53 form a low-pressure circuit.

Die Niederdruckpumpe 51 ist vorzugsweise so ausgelegt, dass sie während des Betriebs der Brennkraftmaschine immer eine ausreichend hohe Kraftstoffmenge liefert, die gewährleistet, dass ein vorgegebener Niederdruck nicht unterschritten wird.The low-pressure pump 51 is preferably designed so that it always supplies a sufficiently high fuel quantity during operation of the internal combustion engine, which ensures that a predetermined low pressure is not exceeded.

Der Zulauf 53 ist hin zu der Hochdruckpumpe 54 geführt, welche ausgangsseitig den Kraftstoff hin zu einem Kraftstoffspeicher 55 fördert. Die Hochdruckpumpe 54 wird in der Regel von der Nockenwelle angetrieben und fördert somit bei konstanter Drehzahl der Kurbelwelle 21 ein konstantes Kraftstoffvolumen in den Kraftstoffspeicher 55.The inlet 53 is guided to the high-pressure pump 54, which promotes the fuel on the output side to a fuel reservoir 55. The high pressure pump 54 is usually driven by the camshaft and thus promotes a constant fuel volume at constant speed of the crankshaft 21 into the fuel accumulator 55.

Die Einspritzventile 34 sind mit dem Kraftstoffspeicher 55 wirkverbunden. Der Kraftstoff wird somit den Einspritzventilen 34 über den Kraftstoffspeicher 55 zugeführt.The injection valves 34 are operatively connected to the fuel reservoir 55. The fuel is thus supplied to the injection valves 34 via the fuel accumulator 55.

In dem Vorlauf der Hochdruckpumpe 54, das heißt stromaufwärts der Hochdruckpumpe 54, ist ein Volumenstromsteuerventil 56 vorgesehen, mittels dessen der Volumenstrom eingestellt werden kann, der der Hochdruckpumpe 54 zugeführt wird. Durch eine entsprechende Ansteuerung des Volumenstromsteuervent i1s 56 kann ein vorgegebener Kraftstoffdruck FUF_SP im Kraftstoffspeicher 55 eingestellt werden.In the flow of the high-pressure pump 54, that is, upstream of the high-pressure pump 54, a volume flow control valve 56 is provided, by means of which the volume flow can be adjusted, which is the high-pressure pump 54 is supplied. By a corresponding control of the volume flow control valve i1s 56, a predetermined fuel pressure FUF_SP in the fuel accumulator 55 can be set.

Zusätzlich ist die Kraftstoffzuführeinrichtung 5 mit einem elektromagnetischen Druckregulator 57 ausgangsseitig des Kraftstoffspeichers 55 und mit einer Rückführleitung in den Niederdruckkreis versehen. Wird ein Kraftstoffdruck im Kraftstoffspeicher 55 größer als der durch entsprechende Ansteuerung des elektromechanischen Druckregulators 57 vorgegebene Kraftstoffdruck FUP_SP, dann öffnet der elektromechanische Druckregulator 57 und Kraftstoff wird aus dem Kraftstoffspeicher 55 in den Niederdruckkreis abgelassen.In addition, the fuel supply device 5 with an electromagnetic pressure regulator 57 on the output side of the fuel accumulator 55 and with a return line in the Low pressure circuit provided. If a fuel pressure in the fuel accumulator 55 is greater than the fuel pressure FUP_SP predetermined by corresponding actuation of the electromechanical pressure regulator 57, the electromechanical pressure regulator 57 opens and fuel is discharged from the fuel accumulator 55 into the low pressure circuit.

Alternativ kann auch das Volumenstromsteuerventil 56 in die Hochdruckpumpe 54 integriert sein, oder der elektromechanische Druckregulator 57 und das Volumenstromsteuerventil 56 werden über einen gemeinsamen Stellantrieb eingestellt, wie es beispielhaft in Figur 2 dargestellt und weiter unten näher erläutert ist.Alternatively, the volume flow control valve 56 may be integrated into the high-pressure pump 54, or the electro-mechanical pressure regulator 57 and the flow control valve 56 are set via a common actuator, as exemplified in FIG. 2 shown and explained in more detail below.

Ferner ist der Brennkraftmaschine eine Steuereinrichtung 6 zugeordnet, der wiederum Sensoren zugeordnet sind, die verschiedene Messgrößen erfassen und jeweils den Messwert der Messgröße ermitteln. Die Steuereinrichtung 6 ermittelt abhängig von mindestens einer der Messgrößen Stellgrößen, die dann in entsprechende Stellsignale zum Steuern von Stellgliedern mittels entsprechender Stellantriebe umgesetzt werden.Furthermore, the internal combustion engine is assigned a control device 6, which in turn are assigned sensors that detect different measured variables and in each case determine the measured value of the measured variable. The control device 6 determines dependent on at least one of the measured variables manipulated variables, which are then converted into corresponding control signals for controlling actuators by means of corresponding actuators.

Die Sensoren sind beispielsweise ein Pedalstellungsgeber, welcher die Stellung eines Fahrpedals erfasst, ein Kurbelwellenwinkelsensor, welcher einen Kurbelwellenwinkel erfasst und welchem dann eine Motordrehzahl zugeordnet wird, ein Luftmassenmesser und ein Kraftstoffdrucksensor 58, welcher einen Kraftstoffdruck FUP_AV in dem Kraftstoffspeicher 55 erfasst. Je nach Ausführungsform der Erfindung kann eine beliebige Untermenge der Sensoren oder auch zusätzliche Sensoren vorhanden sein.The sensors are, for example, a pedal position sensor which detects the position of an accelerator pedal, a crankshaft angle sensor which detects a crankshaft angle and which is then assigned an engine speed, an air mass meter and a fuel pressure sensor 58 which detects a fuel pressure FUP_AV in the fuel accumulator 55. Depending on the embodiment of the invention, any subset of the sensors or additional sensors may be present.

Die Stellglieder sind beispielsweise als Gaseinlass- oder Gasauslassventile, Einspritzventile 34, Zündkerze, Drosselklappe, Niederdruckpumpe 51, Volumenstromsteuerventil 56 oder auch als elektromechanischer Druckregulator 57 ausgebildet.The actuators are designed, for example, as gas inlet or gas outlet valves, injection valves 34, spark plug, throttle valve, low-pressure pump 51, volume flow control valve 56 or else as electromechanical pressure regulator 57.

Bevorzugt hat die Brennkraftmaschine auch weitere Zylinder, denen dann entsprechende Stellglieder zugeordnet sind.Preferably, the internal combustion engine also has other cylinders, which are then assigned corresponding actuators.

Figur 2 zeigt ein Kombinationsventil 7, das einen Stellantrieb 70, das Volumenstromsteuerventil 56 und den elektromechanischen Druckregulator 57 umfasst. Das Kombinationsventil 7 hat einen Auslass 71, der mit dem Einlass der Hochdruckpumpe 54 wirkverbunden ist, einen Anschluss 72, der mit dem Zulauf 53 wirkverbunden ist, und einen Einlass 73, der mit dem Kraftstoffspeicher 55 wirkverbunden ist. Das Volumenstromsteuerventil 56 umfasst den Anschluss 72, den Auslass 71, einen Ventilsteller 74 und den Stellantrieb 70. Der elektromechanische Druckregulator 57 umfasst den Einlass 73, den Anschluss 72, den Ventilsteller 74, eine Feder 75, einen Ventilverschluss 76 und den Stellantrieb 70. FIG. 2 shows a combination valve 7, which includes an actuator 70, the flow control valve 56 and the electro-mechanical pressure regulator 57. The combination valve 7 has an outlet 71 operatively connected to the inlet of the high pressure pump 54, a port 72 operatively connected to the inlet 53, and an inlet 73 operatively connected to the fuel reservoir 55. The flow control valve 56 includes the port 72, the outlet 71, a valve actuator 74, and the actuator 70. The electro-mechanical pressure regulator 57 includes the inlet 73, the port 72, the valve actuator 74, a spring 75, a valve plug 76, and the actuator 70.

Der Stellantrieb 70 bewegt abhängig von einem Stellsignal PWM den Ventilsteller 74 in axialer Richtung. Die Feder 75 ist zwischen dem Ventilsteller 74 und dem Ventilverschluss 76 angeordnet und abhängig von der axialen Position des ventilstellers 74 vorgespannt. Der Ventilsteller 74 ist so ausgebildet, dass in dem Bereich einer ersten axialen Verschiebung des Ventilstellers 74 in Richtung zu der Feder 75 ausgehend von seiner axialen Position, in die er durch die Feder 75 gedrückt wird ohne ein Beaufschlagen des Stellantriebs 70 mit dem Stellsignal PWM, der Kraftstofffluss im Wesentlichen unterbunden ist. In diesem zustand strömt von dem Anschluss 72 lediglich ein Leckfluss hin zu dem Auslass 71. In dem Bereich einer zweiten axialen Verschiebung des Ventilstellers 74 durch ein entsprechendes Beaufschlagen des Stellantriebs 70 mit dem Stellsignal PWM wird der Anschluss 72 mit dem Auslass 71 hydraulisch gekoppelt. Abhängig von dem Stellsignal PWM kann in dem zweiten Bereich der axialen Verschiebung des ventilstellers 74 ein verschieden großer Volumenstrom von dem Zulauf 53 in den Anschluss 72 hin zum Auslass 71 und zu der Hochdruckpumpe 54 fließen.The actuator 70 moves in response to a control signal PWM the valve actuator 74 in the axial direction. The spring 75 is disposed between the valve actuator 74 and the valve closure 76 and biased depending on the axial position of the valve actuator 74. The valve actuator 74 is designed such that, in the region of a first axial displacement of the valve actuator 74 in the direction of the spring 75, starting from its axial position, in which it is pressed by the spring 75, without the actuation of the actuator 70 with the control signal PWM, the fuel flow is substantially prevented. In this state, only a leakage flow from the port 72 to the outlet 71. In the region of a second axial displacement of the valve actuator 74 by a corresponding loading of the actuator 70 with the control signal PWM, the port 72 is hydraulically coupled to the outlet 71. Depending on the control signal PWM, in the second region of the axial displacement of the valve actuator 74, a differently large volume flow can flow from the inlet 53 into the port 72 towards the outlet 71 and to the high-pressure pump 54.

Wenn die durch den Kraftstoffdruck in dem Kraftstoffspeicher 55 hervorgerufene Kraft größer ist als die durch die Vorspannung der Feder hervorgerufene und auf den Ventilverschluss 76 ausgeübte Kraft, wird der Einlass 73 mit dem Anschluss 72 hydraulisch gekoppelt, so dass Kraftstoff von dem Kraftstoffspeicher 55 in den Einlass 73 hin zum Auslass 72 in den Zulauf 53 fließen kann.When the force caused by the fuel pressure in the fuel accumulator 55 is greater than the force exerted by the bias of the spring and applied to the valve closure 76, the inlet 73 is hydraulically coupled to the port 72 such that fuel from the fuel accumulator 55 into the inlet 73 toward the outlet 72 in the inlet 53 can flow.

Der Kraftstoffdruck im Kraftstoffspeicher 55, der zu einem Öffnen des elektromechanischen Druckregulators mindestens erforderlich ist, kann durch Erhöhen oder Verringern des Stellsignals PWM eingestellt werden. Der Stellantrieb 70 erhöht oder verringert entsprechend die Kraft, die über den Ventilsteller 74 auf die Feder 75 einwirkt und die Feder 75 vorspannt. Die durch die Vorspannung der Feder 75 hervorgerufene Kraft schließt den elektromechanischen Druckregulator, wenn die durch den Kraftstoffdruck im Kraftstoffspeicher 55 auf den Ventilverschluss 76 ausgeübte Kraft kleiner ist.The fuel pressure in the fuel accumulator 55, which is at least necessary for opening the electro-mechanical pressure regulator, can be adjusted by increasing or decreasing the control signal PWM. The actuator 70 correspondingly increases or decreases the force that acts on the spring 75 via the valve actuator 74 and biases the spring 75. The force caused by the bias of the spring 75 closes the electro-mechanical pressure regulator when the force exerted by the fuel pressure in the fuel accumulator 55 on the valve closure 76 is smaller.

Figur 3 zeigt Kennlinien des in Figur 2 dargestellten Kombinationsventils 7. Eine Druckkurve 80 zeigt den Zusammenhang zwischen dem Stellsignal PWM in Ampere und dem Kraftstoffdruck im Kraftstoffspeicher 55 in bar. Wird bei gegebenem Stellsignal PWM der Kraftstoffdruck im Kraftstoffspeicher 55 über den durch die Druckkurve 80 vorgegebenen Wert erhöht, so öffnet der elektromechanische Druckregulator 57 und verringert durch Ablassen von Kraftstoff aus dem Kraftstoffspeicher 55 in den Zulauf 53 den Kraftstoffdruck im Kraftstoffspeicher 55. FIG. 3 shows characteristics of the in FIG. 2 A pressure curve 80 shows the relationship between the control signal PWM in amperes and the fuel pressure in the fuel tank 55 in bar. If the fuel pressure in the fuel accumulator 55 is increased above the value predefined by the pressure curve 80 at a given control signal PWM, the electromechanical pressure regulator 57 opens and reduces the fuel pressure in the fuel accumulator 55 by discharging fuel from the fuel accumulator 55 into the inlet 53.

Für Werte des Stellsignals PWM, die größer sind als ein Schwellenwert, der in diesem Ausführungsbeispiel einen Wert von etwa 0,5 Ampere hat, öffnet sich das Volumenstromsteuerventil 56 und ermöglicht einen in Liter pro Minute angegebenen Kraftstofffluss. Das Diagramm zeigt eine obere Flusskurve 81, die eine obere Toleranzgrenze für das Kombinationsventil 7 darstellt, eine untere Flusskurve 82, die eine untere Toleranzgrenze für das Kombinationsventil 7 darstellt, und eine mittlere Flusskurve 83, die den Mittelwert zwischen oberer und unterer Flusskurve darstellt. Die Flusskurven 81, 82 und 83 zeigen, dass bei diesem Ausführungsbeispiel unterhalb des Schwellenwerts, also wenn das Volumenstromsteuerventil 56 im Wesentlichen geschlossen ist, noch der Leckfluss fließen kann.For values of the control signal PWM, which are greater than a threshold, which in this embodiment has a value of about 0.5 amperes, opens the volume flow control valve 56 and allows a specified in liters per minute fuel flow. The diagram shows an upper flow curve 81, which represents an upper tolerance limit for the combination valve 7, a lower flow curve 82, which is a lower tolerance limit for the combination valve 7, and a mean flow curve 83, which represents the mean value between the upper and lower flow curves. The flow curves 81, 82 and 83 show that in this embodiment, below the threshold value, that is, when the volume flow control valve 56 is substantially closed, the leakage flow can still flow.

In Figur 4 ist ein Blockschaltbild einer Regeleinrichtung dargestellt, die zur Regelung des Kraftstoffdrucks in einer Kraftstoffzuführeinrichtung 5 verwendet werden kann, die ein Kombinationsventil 7 umfasst, wie es beispielhaft in Figur 2 ausgeführt ist. Die Regelung des Kraftstoffdrucks im Kraftstoffspeicher 55 erfolgt abhängig davon, in welcher Betriebsart die Kraftstoffzuführeinrichtung 5 aktuell betrieben wird.In FIG. 4 1 is a block diagram of a control device that may be used to control the fuel pressure in a fuel supply device 5 that includes a combination valve 7, as exemplified in FIG FIG. 2 is executed. The regulation of the fuel pressure in the fuel accumulator 55 is dependent on in which mode the fuel supply device 5 is currently operated.

In einer ersten Betriebsart wird der Kraftstoffdruck im Kraftstoffspeicher 55 abhängig von der von der Hochdruckpumpe 54 geförderten Kraftstoffmenge eingestellt. Das Volumenstromsteuerventil 56 ist geöffnet und die geförderte Kraftstoffmenge ist abhängig von der Ansteuerung des Volumenstromsteuerventils 56. In dieser Betriebsart ist der elektromechanische Druckregulator 57 geschlossen. Wenn mehr Kraftstoff in den Kraftstoffspeicher 55 gefördert als zugemessen wird, dann steigt der Kraftstoffdruck im Kraftstoffspeicher 55. Wenn weniger Kraftstoff in den Kraftstoffspeicher 55 gefördert als zugemessen wird, dann sinkt entsprechend der Kraftstoffdruck im Kraftstoffspeicher 55. Diese erste Betriebsart wird Mengenregelung VC genannt.In a first mode, the fuel pressure in the fuel accumulator 55 is adjusted depending on the amount of fuel delivered by the high-pressure pump 54. The volume flow control valve 56 is open and the amount of fuel delivered is dependent on the control of the volume flow control valve 56. In this mode, the electro-mechanical pressure regulator 57 is closed. When more fuel is delivered to the fuel reservoir 55 than is metered, the fuel pressure in the fuel reservoir 55 increases. If less fuel is delivered to the fuel reservoir 55 than is metered, then the fuel pressure in the fuel reservoir 55 decreases correspondingly. This first mode is called volume control VC.

In einer zweiten Betriebsart ist das Volumenstromsteuerventil 56 geschlossen. Durch das Volumenstromsteuerventil 56 fließt nur der Leckfluss. Ist der elektromechanische Druckregulator 57 geschlossen und wird weniger Kraftstoff zugemessen als durch den Leckfluss in den Kraftstoffspeicher 55 gefördert wird, dann steigt der Kraftstoffdruck im Kraftstoffspeicher 55, bis der elektromechanische Druckregulator 57 öffnet und Kraftstoff in den Zulauf 53 absteuert. Dadurch wird der Kraftstoffdruck im Kraftstoffspeicher 55 auf den durch den elektromechanischen Druckregulator 57 vorgegebenen Kraftstoffdruck begrenzt. Diese zweite Betriebsart wird deshalb Druckregelung PC genannt.In a second operating mode, the volume flow control valve 56 is closed. By the flow control valve 56, only the leakage flow. If the electromechanical pressure regulator 57 is closed and less fuel is metered as is conveyed by the leakage flow in the fuel accumulator 55, then the fuel pressure in the fuel accumulator 55 increases until the electro-mechanical pressure regulator 57 opens and Fuel in the inlet 53 absteuert. As a result, the fuel pressure in the fuel accumulator 55 is limited to the fuel pressure predetermined by the electromechanical pressure regulator 57. This second mode is therefore called pressure control PC.

Figur 4 zeigt zwei Regelkreise, zwischen denen abhängig von der aktuell eingestellten Betriebsart der Kraftstoffzuführeinrichtung 5 mittels eines Schalters LV_MS umgeschaltet werden kann. Ist die aktuell eingestellte Betriebsart die erste Betriebsart, also die Mengenreglung VC, dann steht der Schalter LV_MS in der Position VC. Ist die aktuell eingestellte Betriebsart die zweite Betriebsart, also die Druckregelung PC, dann steht der Schalter LV_MS in der Position PC. FIG. 4 shows two control circuits, between which, depending on the currently set operating mode of the fuel supply device 5 by means of a switch LV_MS can be switched. If the currently set operating mode is the first operating mode, ie the quantity control VC, then the switch LV_MS is in the position VC. If the currently set operating mode is the second operating mode, ie the pressure control PC, then the LV_MS switch is in the PC position.

Aus der Differenz zwischen dem vorgegeben Kraftstoffdruck FUP_SP und dem erfassten Kraftstoffdruck FUP_AV wird eine Regeldifferenz FUP_DIF bestimmt. Die Regeldifferenz FUP_DIF wird bei der Mengenregelung VC einem Regler in Block B1 zugeführt. Dieser Regler umfasst mindestens einen Integralanteil I_CTRL und ist vorzugsweise als PI-Regler ausgeführt. In dem Block B1 wird ein Reglerwert FUEL_MASS_FB_CTRL des ersten Reglers bestimmt. Abhängig von dem vorgegebenen Kraftstoffdruck FUP_SP und dem erfassten Kraftstoffdruck FUP_AV wird in einem Block B2 ein Vorsteuerwert FUEL_MASS_PRE der zu fördernden Kraftstoffmasse ermittelt. Der Vorsteuerwert FUEL_MASS_PRE der zu fördernden Kraftstoffmasse, der Reglerwert FUEL_MASS_FB_CTRL des ersten Reglers und die einzuspritzende Kraftstoffmasse MFF werden aufsummiert zu einer zu fördernden Kraftstoffmasse FUEL_MASS_REQ. In einem Block B3 wird abhängig von der zu fördernden Kraftstoffmasse FUEL_MASS_REQ ein Stellsignal PWM_VC bei Mengenregelung VC bestimmt. Der Block B3 umfasst vorzugsweise ein Kennfeld. Ein Block B4 repräsentiert die in Figur 1 dargestellte Kraftstoffzuführeinrichtung 5 mit dem in Figur 2 dargestellten Kombinationsventil 7. Das Stellsignal PWM, das bei Mengenregelung VC gleich dem Stellsignal PWM_VC bei Mengenregelung VC ist, ist die Eingangsgröße des Blocks B4. Die Ausgangsgröße des Blocks B4 ist der erfasste Kraftstoffdruck FUP_AV, der beispielsweise mittels des Kraftstoffdrucksensors 58 erfasst wird.From the difference between the predetermined fuel pressure FUP_SP and the detected fuel pressure FUP_AV, a control difference FUP_DIF is determined. The control difference FUP_DIF is supplied to a controller in block B1 in the quantity control VC. This controller comprises at least one integral component I_CTRL and is preferably designed as a PI controller. In block B1, a controller value FUEL_MASS_FB_CTRL of the first controller is determined. Depending on the predetermined fuel pressure FUP_SP and the detected fuel pressure FUP_AV, a pilot value FUEL_MASS_PRE of the fuel mass to be delivered is determined in a block B2. The pilot value FUEL_MASS_PRE of the fuel mass to be delivered, the controller value FUEL_MASS_FB_CTRL of the first controller and the fuel mass MFF to be injected are added up to a fuel mass FUEL_MASS_REQ to be delivered. In a block B3, depending on the fuel mass FUEL_MASS_REQ to be delivered, an actuating signal PWM_VC is determined during flow control VC. The block B3 preferably includes a map. A block B4 represents the in FIG. 1 shown fuel supply device 5 with the in FIG. 2 shown combination valve 7. The control signal PWM, which is equal to the control signal PWM_VC at volume control VC in volume control, is the Input size of block B4. The output of the block B4 is the detected fuel pressure FUP_AV detected by the fuel pressure sensor 58, for example.

Bei Druckregelung PC wird die Regeldifferenz FUP_DIF einem zweiten Regler in einem Block B5 zugeführt. Der Regler in Block B5 umfasst vorzugsweise einen PI-Regler. In einem Block B6 wird abhängig von dem vorgegebenen Kraftstoffdruck FUP_SP ein Vorsteuerwert PWM_PRE für ein Stellsignal PWM_PC bei Druckregelung PC bestimmt, zu dem ein in dem Block B5 ermittelter Reglerwert PWM_FB_CTRL des zweiten Reglers addiert wird. Die Summe ist das Stellsignal PWM_PC bei Druckregelung PC. Bei Druckregelung PC ist das Stellsignal PWM gleich dem Stellsignal PWM_PC bei Druckregelung PC. Der Block B6 umfasst vorzugsweise ein Kennfeld.For pressure control PC, the control difference FUP_DIF is fed to a second controller in a block B5. The controller in block B5 preferably comprises a PI controller. In a block B6, depending on the predetermined fuel pressure FUP_SP, a pilot control value PWM_PRE for an actuating signal PWM_PC is determined in pressure control PC, to which a controller value PWM_FB_CTRL of the second controller determined in block B5 is added. The sum is the control signal PWM_PC with pressure control PC. With pressure control PC, the control signal PWM is equal to the control signal PWM_PC with pressure control PC. The block B6 preferably includes a map.

Die Kennfelder der Blöcke B3 und B6 werden bevorzugt vorab durch Versuche an einem Motorprüfstand, durch Simulationen oder durch Fahrversuche ermittelt. Alternativ können auch beispielsweise auf physikalischen Modellen basierende Funktionen verwendet werden.The maps of blocks B3 and B6 are preferably determined in advance by tests on an engine test bench, by simulations or by driving tests. Alternatively, for example, functions based on physical models may also be used.

Das in Figur 4 dargestellte Blockdiagramm ist eine bevorzugte Ausführungsform einer Regeleinrichtung für eine Kraftstoffzuführeinrichtung 5 mit einem Kombinationsventil 7 nach Figur 2 und Kennlinien nach Figur 3. Falls das-Volumenstromsteuerventil 56 und der elektromechanische Druckregulator 57 jedoch jeweils einen eigenen Stellantrieb haben, dann wirkt das Stellsignal PNM_VC bei Mengenregelung VC auf den Stellantrieb des volumenstromsteuerventils 56 und das Stellsignal PWM_PC bei Druckregelung PC auf den Stellantrieb des elektromechanischen Druckregulators 57. Dem Block B4 werden folglich anstelle des gemeinsamen Stellsignals PWM sowohl das Stellsignal PWM_VC bei Mengenregelung VC als auch das Stellsignal PWM_PC bei Druckregelung PC zugeführt. Die Regelkreise für die erste und die zweite Betriebsart arbeiten in diesem Fall vorzugsweise parallel, so dass auf den in Figur 4 dargestellten Schalter LV_MS verzichtet werden kann. Den Blöcken B1 und B5 wird gleichzeitig die Regeldifferenz FUP_DIF zugeführt.This in FIG. 4 The block diagram shown is a preferred embodiment of a control device for a fuel supply device 5 with a combination valve 7 after FIG. 2 and characteristics after FIG. 3 , If, however, the volumetric flow control valve 56 and the electromechanical pressure regulator 57 each have their own actuator, then the control signal PNM_VC acts on the actuator of the volume flow control valve 56 and the control signal PWM_PC at pressure control PC on the actuator of the electro-mechanical pressure regulator 57 in the flow control VC. The block B4 Consequently, instead of the common control signal PWM both the control signal PWM_VC supplied with volume control VC and the control signal PWM_PC in pressure control PC. The control circuits for the first and the second mode of operation in this case preferably operate in parallel, so that in the FIG. 4 shown Switch LV_MS can be dispensed with. The blocks B1 and B5 are simultaneously fed with the control difference FUP_DIF.

Figur 5 zeigt ein Ablaufdiagramm zur Erkennung von Fehlern in einer Kraftstoffzuführeinrichtung 5 einer Brennkraftmaschine. Das Verfahren wird in einem Schritt S1 gestartet. Vorzugsweise wird der Schritt S1 beim Start der Brennkraftmaschine ausgeführt. Der Schritt S1 umfasst vorzugsweise weitere, hier nicht dargestellte, Initialisierungsschritte, wie beispielsweise ein Zurücksetzen von Zähleinrichtungen. FIG. 5 shows a flowchart for detecting errors in a fuel supply device 5 of an internal combustion engine. The method is started in a step S1. Preferably, the step S1 is executed at the start of the internal combustion engine. The step S1 preferably comprises further, not shown here, initialization steps, such as a reset of counters.

In einem Schritt S2 wird die Stellung des Schalters LV_MS geprüft. Falls kein Schalter LV_MS vorhanden ist, dann wird in Schritt S2 die aktuelle Betriebsart der Kraftstoffzuführeinrichtung 5 festgestellt.In a step S2, the position of the switch LV_MS is checked. If there is no switch LV_MS, then the current operating mode of the fuel supply device 5 is determined in step S2.

Falls die aktuelle Betriebsart die Druckregelung PC ist, wird in einem Schritt S3 der erfasste Kraftstoffdruck FUP__AV überprüft. Ist der erfasste Kraftstoffdruck FUP_AV größer oder gleich einer vorgegebenen unteren Toleranzgrenze FUP_PMM_BOL für den Kraftstoffdruck FUP_AV und kleiner oder gleich einer vorgegebene oberen Toleranzgrenze FUP_PMW_TOL für den Kraftstoffdruck FUP_AV, so wird aktuell kein Verlassen des durch die Toleranzgrenzen FUP_PWM_BOL und FUP_PWM_TOL vorgegebenen wertebereichs erkannt und die Bearbeitung in einem Schritt S4 fortgesetzt. Liegt der erfasste Kraftstoffdruck FUP_AV in Schritt S3 außerhalb des durch die Toleranzgrenzen FUP_PWM_BOL und FUP_PWM_TOL vorgegebenen Wertebereichs, so kann ein Fehler vorliegen und die Bearbeitung wird in einem Schritt S5 fortgesetzt. In dem Schritt S4 werden beispielsweise die Fehlerzähler überprüft und gegebenenfalls mit einem neuen Wert versehen. Die Fehlerzähler werden beispielsweise um einen vorgegebenen Betrag verringert. Nach dem Schritt S4 wird die Bearbeitung nach einer Wartezeitdauer T_W erneut in dem Schritt S2 fortgeführt. Ist die Bedingung des Schritts S3 nicht erfüllt, so wird in dem Schritt S5 ein Fehlerzähler PWM_ERR_CNT des Stellsignals PWM erhöht, z.B. um eins.If the current mode is the pressure control PC, the detected fuel pressure FUP__AV is checked in a step S3. If the detected fuel pressure FUP_AV is greater than or equal to a predefined lower tolerance limit FUP_PMM_BOL for the fuel pressure FUP_AV and less than or equal to a predetermined upper tolerance limit FUP_PMW_TOL for the fuel pressure FUP_AV, then no exit of the value range specified by the tolerance limits FUP_PWM_BOL and FUP_PWM_TOL is recognized and the processing in a step S4 continues. If the detected fuel pressure FUP_AV is outside the value range specified by the tolerance limits FUP_PWM_BOL and FUP_PWM_TOL in step S3, an error may be present and the processing is continued in a step S5. In step S4, for example, the error counters are checked and optionally provided with a new value. The error counters are reduced by a predetermined amount, for example. After the step S4, the processing after a waiting period T_W is continued again in the step S2. If the condition of step S3 is not met, an error counter PWM_ERR_CNT of the control signal PWM is increased in step S5, for example by one.

Falls die Mengenregelung VC die aktuelle Betriebsart ist, so wird im Anschluss an den Schritt S2 in einem Schritt S6 der Integralanteil I_CTRL des ersten Reglers in Block B1 überprüft. Ist der Integralanteil I_CTRL größer oder gleich einer vorgegebenen unteren Toleranzgrenze I_CTRL_BOL des Integralanteils und kleiner oder gleich einer vorgegebenen oberen Toleranzgrenze I_CTRL__TOL des Integralanteils, dann wird aktuell kein Verlassen des durch die Toleranzgrenzen I_CTRL_BOL und I_CTRL_TOL vorgegebenen Wertebereichs erkannt und die Bearbeitung in dem Schritt S4 fortgesetzt. Andernfalls wird die Bearbeitung in einem Schritt S7 fortgesetzt. Nach dem Schritt S4 wird die Bearbeitung nach der Wartezeitdauer T__W in dem Schritt S2 fortgesetzt. Ist die Bedingung des Schritts S6 nicht erfüllt, dann wird in dem Schritt S7 ein Fehlerzähler I_CTRL_ERR_CNT des Integralanteils I_CTRL erhöht, z.B. um 1.If the quantity control VC is the current operating mode, the integral component I_CTRL of the first controller in block B1 is checked in a step S6 following step S2. If the integral component I_CTRL is greater than or equal to a predetermined lower tolerance limit I_CTRL_BOL of the integral component and less than or equal to a predetermined upper tolerance limit I_CTRL__TOL of the integral component, then no exit of the value range specified by the tolerance limits I_CTRL_BOL and I_CTRL_TOL is detected and the processing is continued in step S4. Otherwise, the processing is continued in a step S7. After the step S4, the processing is continued after the waiting time T__W in the step S2. If the condition of step S6 is not satisfied, then in step S7 an error counter I_CTRL_ERR_CNT of the integral component I_CTRL is increased, e.g. at 1.

Auf das Erhöhen des Fehlerzählers in dem Schritt S5 oder in dem Schritt S7 folgt ein Schritt S8, in dem die Werte der Fehlerzähler überprüft werden. Ist der Fehlerzähler PWM__ERR_CNT des Stellsignals PWM größer oder gleich einer vorgegebenen oberen Fehlergrenze PWM_ERR_CNT_TOL des Fehlerzählers PWM_ERR_CNT des Stellsignals PWM oder ist der Fehlerzähler I_CTRL__ERR_CNT des Integralanteils I_CTRL größer oder gleich einer vorgegebenen oberen Fehlergrenze I_CTRL_ERR_CNT_TOL des Fehlerzählers I_CTRL_ERR_CNT des Integralanteils I_CTRL, dann wird ein Fehler erkannt und in einem Schritt S9 werden Maßnahmen ergriffen, die zum Beispiel den genauen Fehlerort und die Fehlerumstände registrieren und speichern, einen sicheren Betrieb der Brennkraftmaschine sicherstellen und den Fehler an den Fahrer des Kraftfahrzeugs melden. Wird in dem Schritt S8 kein Überschreiten der Fehlergrenzen PWM__ERR_CNT_TOL und I_CTRL_ERR_CNT_TOL festgestellt, so wird die Bearbeitung nach der Wartezeitdauer T_W in dem Schritt S2 fortgeführtThe stepping-up of the error counter in step S5 or step S7 is followed by step S8 in which the values of the error counters are checked. If the error counter PWM_ERR_CNT of the control signal PWM is greater than or equal to a predetermined upper error limit PWM_ERR_CNT_TOL of the error counter PWM_ERR_CNT of the control signal PWM or if the error counter I_CTRL__ERR_CNT of the integral component I_CTRL is greater than or equal to a predetermined upper error limit I_CTRL_ERR_CNT_TOL of the error counter I_CTRL_ERR_CNT of the integral component I_CTRL, then an error is detected and In a step S9 measures are taken which register and store, for example, the exact location of the fault and the fault conditions, ensure safe operation of the internal combustion engine and report the fault to the driver of the motor vehicle. If no exceeding of the error limits PWM__ERR_CNT_TOL and I_CTRL_ERR_CNT_TOL is determined in step S8, the processing is continued after the waiting time T_W in step S2

In einem weiteren, hier nicht dargestellten Ausführungsbeispiel, sind keine Fehlerzähler vorgesehen. In diesem Fall wird ein Fehler unmittelbar erkannt, wenn die Bedingungen in dem Schritt S3 oder in dem Schritt S6 nicht erfüllt sind.In a further embodiment, not shown here, no error counters are provided. In this case, an error is immediately recognized when the conditions in the step S3 or in the step S6 are not satisfied.

Claims (4)

  1. Method for monitoring a fuel supply device (5) pertaining to an internal combustion engine, wherein the fuel supply device (5) comprises:
    - a low pressure circuit,
    - a high pressure pump (54) that is coupled to the low pressure circuit at the input side and conveys the fuel into a fuel accumulator (55),
    - a volume flow control valve (56) associated with the high pressure pump (54), and
    - an electromechanical pressure regulator (57) that is actively connected to the fuel accumulator (55) and the low pressure circuit and can stop the flow of fuel from the fuel accumulator (55) into the low pressure circuit,
    characterised in that
    - in a first operating mode a regulating signal (PWM_VC) for the volume flow control valve is generated by means of a first regulator, wherein the first regulator comprises at least one integral part (I_CTRL) and a difference in a specified fuel pressure (FUP_SP) and a detected fuel pressure (FUP_AV) is supplied to the first regulator as a control deviation (FUP_DIF),
    - in a second operating mode a regulating signal (PWM_PC) for the electromechanical pressure regulator is generated by means of a second regulator, wherein the difference in the specified fuel pressure (FUP_SP) and the detected fuel pressure (FUP_AV) is supplied to the second regulator as the control deviation (FUP_DIF),
    - in the first operating mode an error in the fuel supply device (5) is identified as a function of the integral part (I_CTRL) of the first regulator, and
    - in the second operating mode an error in the fuel supply device (5) is identified as a function of the detected fuel pressure (FUP_AV) and the regulating signal (PWM_PC) for the electromechanical pressure regulator.
  2. Method according to claim 1, characterised in that in the first operating mode an error in the fuel supply device (5) is identified if the integral part (I_CTRL) of the first regulator is less than a specified lower tolerance limit (I_CTRL_BOL) of the integral part (I_CTRL) or is greater than a specified upper tolerance limit (I_CTRL_TOL) of the integral part (I_CTRL).
  3. Method according to claim 1 or 2, characterised in that in the second operating mode an error in the fuel supply device (5) is identified if the detected fuel pressure (FUP_AV) is less than a lower tolerance limit (FUP_PWM_BOL) for the fuel pressure (FUP_AV) specified by the regulating signal (PWM_PC) for the electromechanical pressure regulator or is greater than an upper tolerance limit (FUP_PWM_TOL) for the fuel pressure (FUP_AV) specified by the regulating signal (PWM_PC) for the electromechanical pressure regulator.
  4. Method according to any one of the preceding claims, characterised in that a combination valve (7) is provided which comprises the volume flow control valve (56) and the electromechanical pressure regulator (57) and has a common actuator (70) for the volume flow control valve (56) and the electromechanical pressure regulator (57), and by means of the combination valve (7) the first operating mode is adjusted such that the current value of a common regulating signal (PWM) is in a first value range of the common regulating signal (PWM), or the second operating mode is adjusted such that the current value of the common regulating signal (PWM) is in a second value range of the common regulating signal (PWM) .
EP05708024A 2004-04-05 2005-02-16 Method for monitoring a fuel supply device pertaining to an internal combustion engine Expired - Lifetime EP1735673B1 (en)

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DE102004016724A DE102004016724B4 (en) 2004-04-05 2004-04-05 Method for monitoring a fuel supply device of an internal combustion engine
PCT/EP2005/050672 WO2005098561A1 (en) 2004-04-05 2005-02-16 Method for monitoring a fuel supply device pertaining to an internal combustion engine

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EP1735673A1 (en) 2006-12-27
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US20070213918A1 (en) 2007-09-13
DE102004016724B4 (en) 2009-01-02
DE502005003657D1 (en) 2008-05-21
DE102004016724A1 (en) 2005-10-27

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